EP0595765A1 - Abkantpresse - Google Patents

Abkantpresse Download PDF

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Publication number
EP0595765A1
EP0595765A1 EP93810705A EP93810705A EP0595765A1 EP 0595765 A1 EP0595765 A1 EP 0595765A1 EP 93810705 A EP93810705 A EP 93810705A EP 93810705 A EP93810705 A EP 93810705A EP 0595765 A1 EP0595765 A1 EP 0595765A1
Authority
EP
European Patent Office
Prior art keywords
cheek
wedge
parts
gap
ram
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
EP93810705A
Other languages
German (de)
English (en)
French (fr)
Inventor
Waldemar Krumholz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
M&S Brugg AG
Original Assignee
M&S Brugg AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by M&S Brugg AG filed Critical M&S Brugg AG
Publication of EP0595765A1 publication Critical patent/EP0595765A1/de
Ceased legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D5/00—Bending sheet metal along straight lines, e.g. to form simple curves
    • B21D5/02—Bending sheet metal along straight lines, e.g. to form simple curves on press brakes without making use of clamping means

Definitions

  • the invention relates to a press brake according to the preamble of patent claim 1.
  • Press brakes with a conventional one-piece ram are known to have the disadvantage that without special measures the ram or the upper cheek and the lower cheek bend in opposite directions under load and therefore form an uneven working gap between the upper and lower tool.
  • This disadvantage has a particularly strong effect on large press brakes with a passage of several meters between the stands and especially when machining workpieces, the width of which is considerably smaller than the total working width of the cheeks.
  • a press brake of the type mentioned in the preamble of claim 1 is described in DE-OS 41 38 286.
  • This press brake has an upper cheek forming the ram, which carries the upper tool and the pressing forces are introduced at both ends thereof, and a lower cheek, which rests freely at both ends and which carries the lower tool.
  • the ram which is divided in two in the manner specified, the upper cheek and the lower cheek bend in the same direction under load at the working edge and the bend lines run at least approximately parallel.
  • the flexibility of the lower cheek part adjoining the work station is increased on its side in such a way that this cheek part inevitably assumes a convex shape under load, in contrast to a one-piece part Ram, which is always concave under the same circumstances.
  • a preferred embodiment of the two-part ram consists in that the gaps run straight from the abutment point to the lateral boundary of the ram and are inclined downwards at a certain angle. As a result of this inclination of the gaps, the cross section of the lower cheek part decreases from the center outwards, in accordance with the desired flexibility of the cheek ends.
  • the nominal dimension of the gap width i.e. The gap width measured on the unloaded ram at the cheek ends is relatively small and, in the case of larger press brakes with a passage of several meters in width and maximum press forces of 1000 to 2000 kN, is only about 1 mm in size.
  • a problem with the previous solution with a two-part tappet is to determine the nominal dimension of the gap width in such a way that, under load, the parallelism of the deflection lines for all load cases occurring in practice and for the various parameters of the sheet metal material to be processed is guaranteed within certain dimensional tolerances.
  • This guarantee exists in a wide range of applications.
  • extreme load cases such as the uneven or one-sided loading of the ram when processing sheet metal pieces, the width of which is considerably smaller than the passage width of the press brake, or the processing of very strong sheets, can cause the parallelism of the bending lines of the top and The cheek deviates from the desired norm. This means that the previous solution does not succeed in meeting the high demands placed on the dimensional accuracy of the products even under the difficult conditions mentioned.
  • the object underlying the invention is to provide a press brake of the type mentioned, which avoids the above-mentioned disadvantage of the two-part ram with a fixed nominal dimension of the gap width and thus offers the possibility of achieving the high dimensional accuracy per se with the two-part ram Extend the range of possible stress cases.
  • the occurrence of the frictional connection of the two cheek parts can be varied independently of the load condition of the ram and can be optimally adapted to the different load cases.
  • the adjustability of the degree of free deflection of the lower cheek part consists in that the Gap in the area of each side end of the plunger opens into a wider space in which the two cheek parts have mutually opposing boundary surfaces which run in a wedge shape and between which a suitable wedge is slidably arranged along the space, which, when the plunger is not loaded, has a clearance between the two cheek parts releases and when reaching a certain deflection of the lower cheek part of the adhesion manufactures the two cheek parts, wherein the above-mentioned scope can be changed by moving the wedge.
  • the free deflection of the lower cheek part can be limited to any dimension below the nominal dimension of the gap width.
  • the wedge is preferably displaced with a displacement drive controlled by a position detector.
  • the wedge angle only needs a few, e.g. 5 angular degrees.
  • the wedge is held in its self-locking position under load, so that no longitudinal forces occur which would have to be absorbed by the sliding drive.
  • the wedge angle of the boundary surfaces of the upper and lower cheek part interacting with the wedge can change slightly.
  • the deflections of the two cheek parts do not vary to the same extent at this point when the load changes.
  • the wedge has two superimposed parts, the abutting surface of which is one Cylinder surface with an axis extending transversely to the direction of displacement of the wedge and to the direction of force of the ram. In this way, the two parts of the wedge can move against each other, rotating about the axis of their cylindrical abutting surface, so that the wedge always has a perfect surface contact with the boundary surfaces of the cheek parts under load.
  • the two parts of the wedge are advantageously connected to one another elastically;
  • the elastic connection of the two parts of the wedge is that a screw is inserted in the lower part of the wedge, which passes through the upper part of the wedge with a circumferential clearance and through a ring of elastic material surrounding the screw with the upper part of the Keils is connected.
  • the elastic ring holds the two parts of the wedge together on the one hand in the unloaded state and, on the other hand, returns them to their normal position when there is mutual displacement after the load has been removed.
  • the frame of the press brake is essentially composed of two vertical side walls 1 and a yoke beam 2 which connects the side walls 1 to one another on the upper side.
  • the yoke beam is box-shaped and consists of two vertical longitudinal plates 4 which are connected to one another at the ends by a vertical transverse plate.
  • the side walls 1 are each formed from two upstanding plates 6 and 7, which are arranged at a distance from one another leaving a space 8 and are connected to one another at the top by the yoke beam 2 and at the bottom by a web 9.
  • the active parts of the press brake form a fixed lower beam 10 and an upper beam 11 forming the ram, to which the folding tools can be fastened in a manner not shown.
  • the Supports 12 each with a semi-cylindrical pan 13.
  • a cylindrical pin 14 is anchored at both, stepped ends of the lower beam 10 reaching between the supports 12, and its projecting ends rest in the relevant pans 13 of the supports 12.
  • the upper cheek or the cheek-shaped plunger 11 has an upper cheek part 15 and a lower cheek part 17 adjoining the work station 16.
  • the two cheek parts 15 and 17 abut against each other in the middle of the cheek and are separated on both sides of the butt joint designed as a butt surface 18 by a gap 19 running transversely to the direction of force with a gap width which increases continuously up to the side ends 20 of the ram 11.
  • the upper cheek part 15 of the plunger 11 hangs at its two offset ends on two support members 21, which are articulated on the one hand to the upper cheek part 15 and on the other hand to the piston rod 22 of a power cylinder 23, the articulated axis on the cheek part 15 being 24 and the on the piston rod 18 located hinge axis is designated 25.
  • Each power cylinder 23 is attached to the adjacent cross plate of the yoke beam 2.
  • a spherical butt joint 26 is provided in each case for transmitting the pressing force from the piston rods 22 to the upper cheek part 15 of the plunger 11 and for the selective introduction of force into this cheek part 15. The details of this butt connection are not discussed in more detail here. A detailed description of the same can be found in DE-OS 41 38 285.
  • the two cheek parts 15 and 17 of the plunger 11 are firmly connected to one another on the butt surface 18, specifically by screws 27, which are arranged in flanges 28, 29 provided on both sides of the cheek parts 15, 17.
  • a displaceable wedge 30 is inserted into the gap 19 shown here with an enlarged gap width, with free play, which leaves a play between the two cheek parts 15, 17 when the plunger 11 is unloaded, and when a certain pressing force F p is reached connects the two cheek parts 15, 17 in a force-fitting manner.
  • the free deflection of the lower cheek part 17 is thus limited by the frictional connection at the gap.
  • this is not a direct frictional connection of the gap flanks, but a frictional connection mediated by the wedge 30 between the two cheek parts 15 and 17.
  • FIGS. 2 and 3 show sections of the upper cheek part 15 and the lower cheek part 17 of the two-part tappet 11 at one side end of the same.
  • the between the two cheek parts 15, 17 provided gap 19 opens into a wider space 31, which is formed by a corresponding recess in the upper cheek part 15.
  • the boundary surfaces 32 and 33 which delimit this space 31 above and below, run in a wedge shape with respect to one another, the boundary surface 33 on the cheek part 17 running horizontally, while the delimitation surface 32 on the upper cheek part 15 has the required angular inclination of, for example, 5 °.
  • the displaceable wedge 30 is arranged in the intermediate space 31. This rests on the lower boundary surface 33 and has a clearance 34 with respect to the upper boundary surface 32 when the plunger 11 is not loaded.
  • a toothed rack 35 is mounted thereon, with which a motor-driven spur gear 36 meshes.
  • the motor drive is mounted on a frame 37 which is attached to the lower cheek part 17 of the plunger 11.
  • the frame 37 consists of a mounting plate 38, two side support plates 39, a bearing plate 40 and a yoke plate 41.
  • the mounting plate 38 is screwed onto the lower cheek part 17 laterally.
  • An electric stepper motor 42 stands on the yoke plate 41 and is screwed onto it.
  • the shaft 43 carrying the spur gear 36 is connected at its upper end to the shaft end 45 of the stepping motor 42 by a rigid coupling 44.
  • a self-aligning ball bearing 46 sits on the lower end of the shaft 43.
  • the self-aligning ball bearing 46 is in turn axially displaceably mounted in a slide bush 47 which is screwed onto the bearing plate 40.
  • Two stop screws 48 are provided on the wedge 30 as a counter bearing for the lateral drive pressure exerted on the wedge 30. which lie laterally on the lower cheek part 17 of the plunger 11.
  • Each probe 49 which detect the two ends of the rack 35 individually, serve as the position detector.
  • Each probe 49 is attached to a support plate 39 of the frame 37 with a support bracket 50. With 51 the electrical leads to the probes 49 are designated.
  • the wedge 30 has two superposed parts 55 and 56, the abutting surface 57 of which is a cylindrical surface with an axis extending transversely to the displacement direction 58 of the wedge 30 is.
  • the upper side 59 of the part 56 has an angular inclination which corresponds to that of the boundary surface 32 on the upper cheek part 17 of the ram 11.
  • the two parts 55, 56 of the wedge 30 are elastically connected to each other, namely that a screw 60 is inserted in the lower part 55 of the wedge, which passes through the upper part 56 of the wedge in a stepped bore 61 with a circumferential free space 62 and through one Screw 60 surrounding ring 63 made of elastic material is connected to the upper part 56 of the wedge.
  • the elastic ring 63 By means of the elastic ring 63, the two parts 55, 56 of the wedge 30 are held together in the unloaded state on the one hand and, on the other hand, are returned to their normal position in the event of a mutual displacement under load after the load has ceased to exist.
  • the lower beam can be formed in two parts and can be equipped with means for adjusting the degree of free deflection, or that both the upper and lower beam can be configured as described above in connection has been described with the formation of the upper cheek.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
  • Extrusion Moulding Of Plastics Or The Like (AREA)
EP93810705A 1992-10-26 1993-10-06 Abkantpresse Ceased EP0595765A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4235971A DE4235971C1 (de) 1992-10-26 1992-10-26 Abkantpresse
DE4235971 1992-10-26

Publications (1)

Publication Number Publication Date
EP0595765A1 true EP0595765A1 (de) 1994-05-04

Family

ID=6471276

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93810705A Ceased EP0595765A1 (de) 1992-10-26 1993-10-06 Abkantpresse

Country Status (5)

Country Link
US (1) US5426966A (zh)
EP (1) EP0595765A1 (zh)
JP (1) JP3074585B2 (zh)
CN (1) CN1091081A (zh)
DE (1) DE4235971C1 (zh)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006003500B3 (de) * 2006-01-24 2007-08-16 Ralf Beger Blechabkantvorrichtung

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2782942B1 (fr) * 1998-09-09 2000-12-01 Amada Europ Sa Presse plieuse a tablier inferieur actif
US7013694B1 (en) 2004-05-14 2006-03-21 Steven Don Sims Portable, metal bending apparatus
FR2942980B1 (fr) * 2009-03-13 2011-04-08 Amada Europ Presse plieuse pour le pliage de feuilles
AT512174B1 (de) 2012-02-13 2013-06-15 Trumpf Maschinen Austria Gmbh Biegepresse mit verstellbarem balkenelement
AT514080B1 (de) * 2013-05-10 2014-10-15 Trumpf Maschinen Austria Gmbh Vorrichtung und Verfahren zum Biegen von Blechen
DE102014226519A1 (de) * 2014-12-19 2016-06-23 Sms Group Gmbh Presswerkzeugteil und Vorrichtung zum Beseitigen von Planheitsfehlern an flächigen Halbzeugen
JP7369636B2 (ja) * 2020-02-17 2023-10-26 株式会社アマダ プレスブレーキ及び曲げ加工方法
CN115318890A (zh) * 2022-06-28 2022-11-11 江苏普力重工科技有限公司 一种智能制造卷板机床现场总线控制机构及控制系统

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2541094A1 (de) * 1975-09-15 1977-03-17 Seiji Shiokawa Pressvorrichtung
DE3116379A1 (de) * 1979-12-14 1982-12-23 Bison-Werke Bähre & Greten GmbH & Co KG, 3257 Springe Heizplattenpresse
DE4138286A1 (de) * 1991-11-21 1993-05-27 M & S Brugg Ag Presse

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1539817A (fr) * 1967-07-26 1968-09-20 Promecam Sisson Lehmann Soc Machine hydraulique pour la déformation de métaux en feuilles
GB1308808A (en) * 1969-03-29 1973-03-07 Verrina Spa Hydraulic driving device for sheet metal working presses
SU548352A1 (ru) * 1974-12-11 1977-02-28 Московский Авиационный Технологический Институт Имени К.Э.Циалковского Гидравлический молот
US5067340A (en) * 1988-05-05 1991-11-26 Macgregor Donald C Precision press brake
DE4138285C2 (de) * 1991-11-21 1994-04-07 M & S Brugg Ag Brugg Hydraulische Abkantpresse

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2541094A1 (de) * 1975-09-15 1977-03-17 Seiji Shiokawa Pressvorrichtung
DE3116379A1 (de) * 1979-12-14 1982-12-23 Bison-Werke Bähre & Greten GmbH & Co KG, 3257 Springe Heizplattenpresse
DE4138286A1 (de) * 1991-11-21 1993-05-27 M & S Brugg Ag Presse

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006003500B3 (de) * 2006-01-24 2007-08-16 Ralf Beger Blechabkantvorrichtung

Also Published As

Publication number Publication date
JP3074585B2 (ja) 2000-08-07
US5426966A (en) 1995-06-27
CN1091081A (zh) 1994-08-24
DE4235971C1 (de) 1994-04-07
JPH06218433A (ja) 1994-08-09

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